US20110214528A1 - Flywheel Assembly - Google Patents

Flywheel Assembly Download PDF

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Publication number
US20110214528A1
US20110214528A1 US13/057,783 US200913057783A US2011214528A1 US 20110214528 A1 US20110214528 A1 US 20110214528A1 US 200913057783 A US200913057783 A US 200913057783A US 2011214528 A1 US2011214528 A1 US 2011214528A1
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United States
Prior art keywords
flywheel
assembly
inner body
housing
stator
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Granted
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US13/057,783
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US10069377B2 (en
Inventor
Ian D. Foley
Colin Tarrant
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GKN Hybrid Power Ltd
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Williams Hybrid Power Ltd
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Assigned to WILLIAMS HYBRID POWER LIMITED reassignment WILLIAMS HYBRID POWER LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FOLEY, IAN DAVID, TARRANT, COLIN
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/04—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow radial displacement, e.g. Oldham couplings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/02—Additional mass for increasing inertia, e.g. flywheels
    • H02K7/025—Additional mass for increasing inertia, e.g. flywheels for power storage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/14—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions combined with a friction coupling for damping vibration or absorbing shock
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/30—Flywheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/30—Flywheels
    • F16F15/315—Flywheels characterised by their supporting arrangement, e.g. mountings, cages, securing inertia member to shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/30—Flywheels
    • F16F15/315—Flywheels characterised by their supporting arrangement, e.g. mountings, cages, securing inertia member to shaft
    • F16F15/3153—Securing inertia members to the shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2121—Flywheel, motion smoothing-type
    • Y10T74/2132—Structural detail, e.g., fiber, held by magnet, etc.

Definitions

  • the present invention relates to a flywheel assembly and more particularly to reduction of the loads experienced during failure of a high speed flywheel.
  • weight of a flywheel assembly it is desirable for the weight of a flywheel assembly to be minimised. This generally makes the assembly easier to transport. More particularly, in mobile applications such as use in vehicles, weight reduction becomes particularly beneficial.
  • the assembly does though need to be sufficiently robust to withstand loads generated during failure of a flywheel rotating at high speed.
  • the present invention provides a flywheel assembly comprising a housing, a flywheel rotatably mounted in the housing and having an inner and an outer circumferential surface, and an inner body spaced radially and inwardly from the inner is circumferential surface of the flywheel, wherein the flywheel rotates in use around and relative to the inner body, the assembly defines an engagement surface spaced radially and outwardly from the outer circumferential surface of the flywheel, and the inner body is flexibly coupled to the housing, such that if the flywheel mounting fails during rotation at speed leading to displacement of the flywheel, flexure of the coupling as a result of forces exerted on the inner body by the displaced flywheel allows the flywheel to contact the engagement surface.
  • the flywheel may form the rotor of a motor whilst the inner body forms its stator.
  • the flexible coupling between the inner body and the housing comprises flexible polymeric material.
  • the flexibility may be provided by an arrangement of one or more springs.
  • FIG. 1 is a cut-away perspective view of a flywheel assembly
  • FIG. 2 is a diagram representing a transverse cross-sectional view of a flywheel assembly embodying the invention
  • FIG. 3 is a cross-sectional view of a flexible stator mounting according to one embodiment of the invention.
  • FIG. 4 is a perspective view of a flexible stator mounting according to another embodiment of the invention.
  • FIG. 5 is a graph plotting radial force and precession frequency against time during a flywheel failure.
  • the flywheel assembly shown in FIG. 1 comprises a rotor 1 formed of magnetically loaded composite material.
  • the rotor has an inner and an outer section ( 1 a and 1 b , respectively).
  • the inner section comprises glass fibres and magnetic particles whilst the outer comprises carbon filaments.
  • the two sections are bonded together.
  • the rotor 1 is rigidly connected to a composite end cap 2 .
  • the end cap is mounted on a shaft 3 , which is located on ceramic bearings 4 .
  • the bearings are supported by a housing or containment 5 . This includes a back plate 5 a and a cylindrical drum 5 b .
  • the inner section la of the rotor forms the permanent magnet component of a motor.
  • the motor also includes a stator 6 mounted on the housing via a stator mount 7 .
  • the stator provides the electrical power to drive and brake the flywheel.
  • the rotor runs within a vacuum chamber 8 , and the stator is oil-cooled by oil circulating via chamber 9 defined by the stator can 10 .
  • the flywheel has two primary failure modes. One is “burst failure”, where the composite outer section of the rotor fails. The other is “intact rotor failure”, where the composite outer section of the rotor remains intact, but either the bearings 4 fail or the composite end cap 2 fails. In the latter case, the rotor spins at high velocity without being constrained by the shaft 3 . The resulting vibration loads transmitted to the flywheel mountings can be substantial. The present invention seeks to considerably reduce these loads.
  • stator mount 7 is a rigid structure rigidly mounted on the housing.
  • the stator is flexibly coupled to the assembly housing.
  • the rotor is displaced from it normal location relative to the housing, and contacts the outside diameter of the internally mounted stator. Friction between these two components causes the rotor to start a precession motion around the stator.
  • the force generated by the rotor's precession also increases, causing the rotor bore and the stator's casing to wear away, increasing the radial clearance.
  • Mounting the stator on suitably designed flexible mountings allows the rotor to move over radially such that the outer diameter of the rotor contacts the inside of the housing.
  • Friction generated between the rotor and the housing generates a precession motion in the opposite direction to the motion caused by contact with the stator, thereby suppressing an increase in the precession frequency. This reduces the radial force that is generated during the failure.
  • the magnitude of the forces generated are governed by the stiffness of the flexible mounting, the initial clearance between the outside diameter of the rotor and the bore of the housing, and the initial clearance between the outside diameter of the stator and the bore of the rotor.
  • the lower the stiffness of the mounting the lower the precession frequency and hence the lower the forces.
  • the stiffness has to be selected such that the natural frequency of the stator mountings does not influence the normal operation of the flywheel energy storage system. To this end, suitable radial damping may be incorporated into the design of the mounting.
  • FIG. 2 shows a cross-sectional view of a flywheel assembly in which an intact rotor s failure has occurred.
  • this results in anti-clockwise precession of the point of contact 22 between the rotor and the stator 24 , and a clockwise precession 28 of the point of contact 26 between the rotor and the surrounding housing 30 .
  • FIG. 3 shows an implementation of a flexible stator mount 32 using moulded polymer mounts.
  • the stator 24 is located on a cylindrical support 34 .
  • the support 34 is coupled to a rigid hub 36 via rubber mountings 38 .
  • the mountings 38 may be cast in PDMS (or another flexible material compatible with the oil used to cool the stator, such as silicon oil), and are bonded to an outer circumferential surface of the hub 36 and an inner circumferential surface of the support 34 .
  • the rubber mountings are 10 mm thick in the radial direction and 20 mm wide in the longitudinal direction. Such an arrangement may produce a radial stiffness of 2500 N/mm with a radial movement of 5 mm.
  • Holes 40 are provided in a flange 42 at one end of the hub 36 for fixing the hub to the back plate of the flywheel housing.
  • the back plate may be profiled to engage with the inner diameter 44 of the hub to assist its location and retention on the back plate.
  • a retaining collar 46 is held on the outer circumferential surface of the hub by grub screws, at the end of the hub opposite to the flange 42 .
  • FIG. 4 depicts an alternative flexible stator mount 50 using a homogenous steel construction in which curved leaf spring elements 52 form the flexible mountings.
  • An inner cylindrical hub element 56 is mounted rigidly onto the flywheel housing.
  • the stator (not shown) is located on the outer circumferential surface of support element 54 .
  • the spring elements 52 extend between the hub and support elements.
  • FIG. 5 is a graph representing the behaviour of a flywheel assembly embodying the invention during an intact rotor failure. It can be seen that the sudden radial force increase associated with the rotor failure is rapidly decreased, as is the associated precession frequency.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Power Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)

Abstract

A flywheel assembly is provided which comprises a housing, a flywheel rotatably mounted in the housing and defining an inner and an outer circumferential surface, and an inner body spaced radially and inwardly from the inner circumferential surface of the flywheel. The flywheel rotates in use around and relative to the inner body, the assembly defines an engagement surface spaced radially and outwardly from the outer circumferential surface of the flywheel, and the inner body is flexibly coupled to the housing. If the flywheel mounting fails during rotation at speed leading to displacement of the flywheel, flexure of the coupling as a result of forces exerted on the inner body by the displaced flywheel allows the flywheel to contact the engagement surface.

Description

  • The present invention relates to a flywheel assembly and more particularly to reduction of the loads experienced during failure of a high speed flywheel.
  • It is desirable for the weight of a flywheel assembly to be minimised. This generally makes the assembly easier to transport. More particularly, in mobile applications such as use in vehicles, weight reduction becomes particularly beneficial. The assembly does though need to be sufficiently robust to withstand loads generated during failure of a flywheel rotating at high speed.
  • The present invention provides a flywheel assembly comprising a housing, a flywheel rotatably mounted in the housing and having an inner and an outer circumferential surface, and an inner body spaced radially and inwardly from the inner is circumferential surface of the flywheel, wherein the flywheel rotates in use around and relative to the inner body, the assembly defines an engagement surface spaced radially and outwardly from the outer circumferential surface of the flywheel, and the inner body is flexibly coupled to the housing, such that if the flywheel mounting fails during rotation at speed leading to displacement of the flywheel, flexure of the coupling as a result of forces exerted on the inner body by the displaced flywheel allows the flywheel to contact the engagement surface.
  • Allowing the flywheel to come into contact with both inner and outer surfaces considerably reduces the loads generated by flywheel failure.
  • In some embodiments, the flywheel may form the rotor of a motor whilst the inner body forms its stator.
  • Preferably, the flexible coupling between the inner body and the housing comprises flexible polymeric material. Alternatively, the flexibility may be provided by an arrangement of one or more springs.
  • Embodiments of the invention will now be described by way of example and with reference to the accompanying schematic drawings wherein:
  • FIG. 1 is a cut-away perspective view of a flywheel assembly;
  • FIG. 2 is a diagram representing a transverse cross-sectional view of a flywheel assembly embodying the invention;
  • FIG. 3 is a cross-sectional view of a flexible stator mounting according to one embodiment of the invention.
  • FIG. 4 is a perspective view of a flexible stator mounting according to another embodiment of the invention; and is FIG. 5 is a graph plotting radial force and precession frequency against time during a flywheel failure.
    •
  • The flywheel assembly shown in FIG. 1 comprises a rotor 1 formed of magnetically loaded composite material. The rotor has an inner and an outer section (1 a and 1 b, respectively). The inner section comprises glass fibres and magnetic particles whilst the outer comprises carbon filaments. The two sections are bonded together.
  • The rotor 1 is rigidly connected to a composite end cap 2. The end cap is mounted on a shaft 3, which is located on ceramic bearings 4. The bearings are supported by a housing or containment 5. This includes a back plate 5 a and a cylindrical drum 5 b.
  • The inner section la of the rotor forms the permanent magnet component of a motor. The motor also includes a stator 6 mounted on the housing via a stator mount 7. The stator provides the electrical power to drive and brake the flywheel. The rotor runs within a vacuum chamber 8, and the stator is oil-cooled by oil circulating via chamber 9 defined by the stator can 10.
  • The flywheel has two primary failure modes. One is “burst failure”, where the composite outer section of the rotor fails. The other is “intact rotor failure”, where the composite outer section of the rotor remains intact, but either the bearings 4 fail or the composite end cap 2 fails. In the latter case, the rotor spins at high velocity without being constrained by the shaft 3. The resulting vibration loads transmitted to the flywheel mountings can be substantial. The present invention seeks to considerably reduce these loads.
  • In the flywheel assembly depicted in FIG. 1, stator mount 7 is a rigid structure rigidly mounted on the housing. In flywheel assemblies embodying the invention, the stator is flexibly coupled to the assembly housing. During an intact rotor failure, the rotor is displaced from it normal location relative to the housing, and contacts the outside diameter of the internally mounted stator. Friction between these two components causes the rotor to start a precession motion around the stator. As the is precession frequency increases, the force generated by the rotor's precession also increases, causing the rotor bore and the stator's casing to wear away, increasing the radial clearance. Mounting the stator on suitably designed flexible mountings allows the rotor to move over radially such that the outer diameter of the rotor contacts the inside of the housing.
  • Friction generated between the rotor and the housing generates a precession motion in the opposite direction to the motion caused by contact with the stator, thereby suppressing an increase in the precession frequency. This reduces the radial force that is generated during the failure.
  • The magnitude of the forces generated are governed by the stiffness of the flexible mounting, the initial clearance between the outside diameter of the rotor and the bore of the housing, and the initial clearance between the outside diameter of the stator and the bore of the rotor. The lower the stiffness of the mounting, the lower the precession frequency and hence the lower the forces. The stiffness has to be selected such that the natural frequency of the stator mountings does not influence the normal operation of the flywheel energy storage system. To this end, suitable radial damping may be incorporated into the design of the mounting.
  • FIG. 2 shows a cross-sectional view of a flywheel assembly in which an intact rotor s failure has occurred. With the rotor 20 rotating anti-clockwise, this results in anti-clockwise precession of the point of contact 22 between the rotor and the stator 24, and a clockwise precession 28 of the point of contact 26 between the rotor and the surrounding housing 30.
  • to FIG. 3 shows an implementation of a flexible stator mount 32 using moulded polymer mounts.
  • The stator 24 is located on a cylindrical support 34. The support 34 is coupled to a rigid hub 36 via rubber mountings 38.
  • The mountings 38 may be cast in PDMS (or another flexible material compatible with the oil used to cool the stator, such as silicon oil), and are bonded to an outer circumferential surface of the hub 36 and an inner circumferential surface of the support 34.
  • In one embodiment, the rubber mountings are 10 mm thick in the radial direction and 20 mm wide in the longitudinal direction. Such an arrangement may produce a radial stiffness of 2500 N/mm with a radial movement of 5 mm.
  • Holes 40 are provided in a flange 42 at one end of the hub 36 for fixing the hub to the back plate of the flywheel housing.
  • The back plate may be profiled to engage with the inner diameter 44 of the hub to assist its location and retention on the back plate. A retaining collar 46 is held on the outer circumferential surface of the hub by grub screws, at the end of the hub opposite to the flange 42.
  • FIG. 4 depicts an alternative flexible stator mount 50 using a homogenous steel construction in which curved leaf spring elements 52 form the flexible mountings. An inner cylindrical hub element 56 is mounted rigidly onto the flywheel housing. The stator (not shown) is located on the outer circumferential surface of support element 54. The spring elements 52 extend between the hub and support elements.
  • FIG. 5 is a graph representing the behaviour of a flywheel assembly embodying the invention during an intact rotor failure. It can be seen that the sudden radial force increase associated with the rotor failure is rapidly decreased, as is the associated precession frequency.
  • It will be appreciated that although embodiments of the invention are described above which include a motor rotor and stator, the approaches described are also applicable to flywheels having a drive system (either mechanical or electrical) mounted externally, is with a shaft driving the flywheel. In this case, the stator may be replaced by a rigid element which would react to the failure loads in a similar way.

Claims (7)

1. A flywheel assembly comprising a housing, a flywheel rotatably mounted in the housing and defining an inner and an outer circumferential surface, and an inner body spaced radially and inwardly from the inner circumferential surface of the flywheel, wherein the flywheel rotates in use around and relative to the inner body, the assembly defines an engagement surface spaced radially and outwardly from the outer circumferential surface of the flywheel, and the inner body is flexibly coupled to the housing, such that if the flywheel mounting fails during rotation at speed leading to displacement of the flywheel, flexure of the coupling as a result of forces exerted on the inner body by the displaced flywheel allows the flywheel to contact the engagement surface.
2. An assembly of claim 1, wherein the flexible coupling extends radially inwardly away from the inner body.
3. An assembly of claim 1, wherein the flywheel provides the rotor of a motor whilst the inner body provides its stator.
4. An assembly of claim 3, wherein the flexible coupling extends radially inwardly away from the stator.
5. An assembly of claim 1, wherein the flexible coupling comprises flexible polymeric material.
6. An assembly of claim 1, wherein the flexible coupling comprises an arrangement of one or more springs.
7. An assembly of claim 5, wherein the flexible coupling between the inner body and the housing comprises an arrangement of one or more curved leaf springs.
US13/057,783 2008-08-18 2009-08-13 Flywheel assembly Active 2031-12-01 US10069377B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB0815067A GB2462671B (en) 2008-08-18 2008-08-18 Flywheel assembly with flexible coupling to enhance safety during flywheel failure
GB0815067.4 2008-08-18
PCT/GB2009/051020 WO2010020806A1 (en) 2008-08-18 2009-08-13 Flywheel assembly

Publications (2)

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US20110214528A1 true US20110214528A1 (en) 2011-09-08
US10069377B2 US10069377B2 (en) 2018-09-04

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US (1) US10069377B2 (en)
EP (1) EP2313667B1 (en)
JP (1) JP5490121B2 (en)
CN (1) CN102124249B (en)
DK (1) DK2313667T3 (en)
ES (1) ES2422932T3 (en)
GB (1) GB2462671B (en)
PL (1) PL2313667T3 (en)
PT (1) PT2313667E (en)
WO (1) WO2010020806A1 (en)

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US9108625B2 (en) 2012-04-05 2015-08-18 Denso Corporation Power transmitting apparatus for vehicle
US20170037932A1 (en) * 2014-04-07 2017-02-09 S4 Energy B.V. A Flywheel System
US10449864B2 (en) 2014-04-15 2019-10-22 Borgwarner Inc. Motor/energy generator and energy storage device combination

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CN104067024B (en) * 2012-03-15 2016-01-13 罗特尼克香港有限公司 There is the dynamo-electric flywheel of safeguard construction
GB2504217B (en) * 2013-07-19 2016-09-14 Gkn Hybrid Power Ltd Flywheels for energy storage and methods of manufacture thereof
GB2504218B (en) 2013-07-19 2016-09-14 Gkn Hybrid Power Ltd Flywheels for energy storage and methods of manufacture thereof
CN108506653A (en) * 2018-03-30 2018-09-07 常州卡斯特铝精密铸造科技有限公司 Bell housing

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US4244240A (en) * 1976-12-17 1981-01-13 The Johns Hopkins University Elastic internal flywheel gimbal
US4679761A (en) * 1981-10-21 1987-07-14 The Johns Hopkins University Vibration dissipation mount for motors or the like
US4647803A (en) * 1983-12-28 1987-03-03 Papst-Motoren Gmbh & Co. Kg Electric motor, particularly a brushless direct current motor
US4617484A (en) * 1984-02-02 1986-10-14 U.S. Philips Corporation Electric motor with a torsionally flexible rotor mount
US4783608A (en) * 1986-06-27 1988-11-08 Etudes Techniques Et Representations Industrielles E.T.R.I. Electric motor with an improved bearing
US5235227A (en) * 1991-01-23 1993-08-10 Panavision International L.P. Noise and vibration dampened electric motor such as for use with a sound movie camera
US5363003A (en) * 1991-06-06 1994-11-08 Nippon Densan Corporation Motor and circuitry for protecting same
US5760508A (en) * 1993-07-06 1998-06-02 British Nuclear Fuels Plc Energy storage and conversion devices
US6809898B1 (en) * 2000-01-13 2004-10-26 Maxtor Corporation Disk drive rocking mode vibration damper
US20030061898A1 (en) * 2001-09-13 2003-04-03 Brackett Norman C. Crash management system for implementation in flywheel systems
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US9108625B2 (en) 2012-04-05 2015-08-18 Denso Corporation Power transmitting apparatus for vehicle
US20170037932A1 (en) * 2014-04-07 2017-02-09 S4 Energy B.V. A Flywheel System
US10907701B2 (en) * 2014-04-07 2021-02-02 S4 Energy B.V. Flywheel system
US10449864B2 (en) 2014-04-15 2019-10-22 Borgwarner Inc. Motor/energy generator and energy storage device combination

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WO2010020806A1 (en) 2010-02-25
JP2012500617A (en) 2012-01-05
PT2313667E (en) 2013-06-03
CN102124249A (en) 2011-07-13
PL2313667T3 (en) 2013-08-30
JP5490121B2 (en) 2014-05-14
GB2462671B (en) 2010-12-15
CN102124249B (en) 2013-03-06
GB0815067D0 (en) 2008-09-24
ES2422932T3 (en) 2013-09-16
US10069377B2 (en) 2018-09-04
EP2313667B1 (en) 2013-03-06
GB2462671A (en) 2010-02-24
DK2313667T3 (en) 2013-06-03
EP2313667A1 (en) 2011-04-27

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